CN1472425A - Operation of two stroke reciprocal IC engine - Google Patents
Operation of two stroke reciprocal IC engine Download PDFInfo
- Publication number
- CN1472425A CN1472425A CNA031471935A CN03147193A CN1472425A CN 1472425 A CN1472425 A CN 1472425A CN A031471935 A CNA031471935 A CN A031471935A CN 03147193 A CN03147193 A CN 03147193A CN 1472425 A CN1472425 A CN 1472425A
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- Prior art keywords
- scavenging
- cylinder
- air
- firing chamber
- combustion engine
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- 230000002000 scavenging effect Effects 0.000 claims abstract description 101
- 238000002485 combustion reaction Methods 0.000 claims abstract description 56
- 238000000034 method Methods 0.000 claims abstract description 43
- 239000000446 fuel Substances 0.000 claims abstract description 9
- 238000010304 firing Methods 0.000 claims description 83
- 239000007789 gas Substances 0.000 claims description 20
- 239000002912 waste gas Substances 0.000 claims description 16
- 230000006835 compression Effects 0.000 claims description 8
- 238000007906 compression Methods 0.000 claims description 8
- 239000007921 spray Substances 0.000 claims description 4
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 238000002347 injection Methods 0.000 abstract 1
- 239000007924 injection Substances 0.000 abstract 1
- 238000011017 operating method Methods 0.000 abstract 1
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 11
- 239000003546 flue gas Substances 0.000 description 11
- 238000007599 discharging Methods 0.000 description 5
- 239000000567 combustion gas Substances 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 230000005611 electricity Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/028—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation for two-stroke engines
- F02D13/0284—Variable control of exhaust valves only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/08—Modifying distribution valve timing for charging purposes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/028—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation for two-stroke engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Provided is an operating method for a two-stroke reciprocating internal combustion engine, particularly a two-stroke large diesel engine, and to provide the reciprocating internal combustion engine operated by this method. The two-stroke reciprocating internal combustion engine comprises cylinders having outlet valves and scavenging apertures, in which pistons are reciprocated along running surfaces between a bottom dead center and a top dead center, and supercharger groupsequipped with turbines driven by exhaust gas from combustion chambers of the cylinders and having rotors for compressing air. Compressed air is supplied as scavenging air to the combustion chambers of the cylinders through the scavenging apertures. The outlet valves are opened first and are closed, as well as before subsequent combustion, after fuel injection before subsequent introduction of scavenging air into the combustion chambers of the cylinders and at a scavenge previous stage when rotational speed is lower than at least a predetermined speed.
Description
Technical field
The present invention relates to the method for work of a kind of two-stroke reciprocating combustion engine, particularly a kind of large-scale diesel engine and relate to a kind of according to the two-stroke reciprocating combustion engine of this method work, particularly a kind of large-scale diesel engine.
Background technique
In order to increase reciprocating internal combustion engine, power that for example be used for boats and ships or that produce the two-stroke large diesel engine of the stationary power generation factory that electric energy uses, fresh air is by a pressure booster set that is typically designed to an exhaust-gas turbocharger after a burn cycle, the part in the heat energy of waste gas of firing chamber of cylinder is left in utilization after this burn cycle, be introduced into the firing chamber of cylinder under the pressure that increases.For this purpose, hot waste gas is supplied with pressure booster set by opening an outlet valve from the firing chamber of cylinder.This pressure booster set is made of a turbine substantially, and this turbine is driven by the hot waste gas that enters pressure booster set under pressure.This turbine drives a rotor then, thereby fresh air is inhaled into and compresses.Diffuser, one have the air-cooler of a water-separator and an air inlet receiver and are placed on this and have a downstream as the turbine of the rotor of compressor, and such setting type is commonly referred to turbosupercharger.From here, compressed fresh air is also referred to as pressurized air or scavenging air, finally is conveyed in each cylinder of large-scale diesel engine.According to the type of large-scale diesel engine, the diverse location that infeeds at cylinder of air carries out.For example for having longitudinally scavenged two stroke engine, the firing chamber that the scavenging groove in the operation surface of the lower area of air by being arranged in cylinder is introduced cylinder.For four stroke engine, the firing chamber that this pressurized air is introduced cylinder by one or more suction valves that are arranged in the cylinder head usually, two stroke engine is equipped with suction valve in cylinder head, with the scavenging groove in the lower area that is substituted in cylinder, also be known.
Because the turbine of pressure booster set is only driven by the hot waste gas of overflowing from the firing chamber of cylinder, so known pressure booster set can only be with lower efficient work, particularly after just starting soon or when being lower than certain rotational speed limit of motor, all the more so.Therefore, pressure booster set is often attached one or more additional hydraulic boosters machinery or electricity, increases so that be issued to a corresponding torque at described rotational speed limit.Hydraulic booster sucks air from first Room that is arranged in the air-cooler downstream usually, and air is sent in one second Room, air is gone into cylinder from this second Room by the scavenging concentrated flow then, is that the backflow block piece of sheet shaped piece prevents the backflow of air to this first Room by form usually.Such hydraulic booster is usually designed to each and all has electric blower up to the electric power of 200kW, and support or replace the exhaust-gas turbocharger that is lower than rotational speed limit, the 10%-50% that it only reaches the full load power of large-scale diesel engine usually is specially 30%-35%.If surpass rotational speed limit, just can save this additional electric hydraulic booster, promptly turn-off hydraulic booster, only come supercharged engine by exhaust-gas turbocharger.In this working state, promptly after turn-offing hydraulic booster, above-mentioned sheet shaped piece is opened, thereby allows pressurized air directly to overflow to second Room from first Room that is arranged in the air-cooler downstream, and air is supplied to the scavenging groove from second Room.
The shortcoming of following the use hydraulic booster to support exhaust-gas turbocharger and producing is self-evident.
Even in low loading range, support exhaust-gas turbocharger to realize the improvement in the cylinder scavenging by using hydraulic booster, however, the firing chamber of cylinder is only by scavenging deficiently, thereby in burn cycle subsequently, can not get the fresh air of q.s, perhaps in known two stroke cycle process, in low loading range, when being lower than certain rotational speed limit, infeed the fresh air of too many amount to the firing chamber.This means that the air quantity of being supplied with can not the controlled or adjusting with the known procedure of the work that is used for reciprocating internal combustion engine.
Except the acquisition expenses that is used for hydraulic booster, also the additional device of the control and/or the adjusting that are used for them must be installed.The design of air inlet receiver is a relative complex because above-mentioned in the work of hydraulic booster indispensable sheet shaped piece as the backflow block piece be complicated.Additional assembling certainly need be relevant with the surcharge of working resource, machine accessory and manpower additional service and repairing effort.In addition, hydraulic booster and air inlet receiver occupied relative big space by separated one first space of sheet shaped piece with one second space dividing, this is normally expensive, and causes the weight of adding.In addition, from energy point of view, it also is disadvantageous carrying out work with hydraulic booster, because for example this must obtain to be used for the required electric energy of electric hydraulic booster work.This means that the work of hydraulic booster finally causes increasing fuel consumption, this also has the reason of additional weight.
Summary of the invention
Therefore, an object of the present invention is to provide the method for work of a kind of two-stroke reciprocating combustion engine, particularly a kind of two-stroke large diesel engine, it is special to allow reciprocating internal combustion engine more efficiently work in low loading range that is lower than a predetermined rotational speed limit, and does not need essential for this reason additional machinery, electric or other assisted turbocharger.In addition, the reciprocating internal combustion engine that the purpose of this invention is to provide work according to the present invention.
Of the present inventionly satisfy these and be characterised in that the feature of the independent claims of corresponding kind at technological method with at the theme of the purpose aspect the equipment.
Corresponding dependent claims relates to particularly advantageous embodiment of the present invention.
Therefore, according to the present invention, provide the method for work of a kind of two-stroke reciprocating combustion engine, particularly a kind of large-scale diesel engine.Two-stroke reciprocating combustion engine comprises a cylinder and a pressure booster set, this cylinder has an outlet valve and a scavenging air openings, in this cylinder, be furnished with one and can between a lower dead point position and a upper dead center position, move surperficial pistons reciprocating along one, this pressure booster set has one by being used for compressed-air actuated rotor from the exhaust-driven turbine of the firing chamber of cylinder and one, pressurized air is supplied with the firing chamber of cylinder with air openings by a scavenging, carry out that fuel sprays and with after-combustion after and before scavenging enters the firing chamber of cylinder subsequently with air, outlet valve is opened earlier in a pre-scavenging phase place, when being lower than at least one predefined rotational speed limit, close then.
The method according to this invention is preferred for a kind of two-stroke large diesel engine, particularly a kind of under a predefined rotational speed limit, for example have in the work of crosshead large-scale diesel engine of prolongation scavenging after starting this large-scale diesel engine.Under a predefined rotational speed limit, a turbosupercharger that is transferred hot waste gas can't provide required power, this turbosupercharger under conventional situation by additional drums blower fan support normally electricity operation and that be designed to assisted turbocharger.Can save such additional drums blower fan by using the method according to this invention.
In an advantageous variant form of the method according to this invention, scavenging is supplied with the firing chamber of cylinder with the scavenging of air by forming the scavenging groove in the cylinder wall with air openings, and promptly this large-scale diesel engine is designed to one and has the two stroke engine that prolongs scavenging.The use of this method is not limited to have the two stroke engine that prolongs scavenging in this respect.In a method according to the present invention, carry out that fuel sprays and with after-combustion after and before scavenging enters the firing chamber of cylinder subsequently with air, outlet valve is opened earlier when being lower than at least one predefined rotational speed limit and then is closed in a pre-scavenging phase place.After one is the compression cycle of burning subsequently, in the firing chamber of the cylinder of reciprocating internal combustion engine, can obtain being in the hot combustion gas under the working pressure, thus make piston in an expansion cycle in known manner to lower dead point position direction motion corresponding to one 180 ° crank angle.The lower dead point position of piston is represented with one 180 ° crank angle as usual, has a maximum volume in this position by the firing chamber of cylinder, cylinder head and pistons delimit, the upper dead center position of piston then represents to have a minimum volume in this firing chamber, position with the crank angle of 0 ° or 360 °.Outlet valve is static at once closing after combustion process.In a pre-scavenging phase place of following this burning, piston discharges the scavenging groove for the first time after this burning before, outlet valve is opened at place, predefined first crank angle, this first crank angle is so to select, thereby when outlet valve is opened, between the firing chamber of cylinder and flue gas leading, have pressure difference, this flue gas leading is applicable to supplies with pressure booster set with the combustion gas from the firing chamber of cylinder, thereby hot waste gas is because this pressure difference enters turbosupercharger by flue gas leading, and at that driving turbine, thereby driving rotor, therefore can obtain as the scavenging of the firing chamber that is used for the introducing cylinder pressurized air with air, the scavenging groove of this cylinder is discharged by corresponding piston simultaneously.This means, the part in the heat energy of waste gas by known way be utilized, by before discharging the scavenging groove, promptly scavenging flows into the firing chamber of cylinder with air before, open outlet valve and driven the turbine of turbosupercharger.
If the pressure difference between firing chamber and flue gas leading is compensated substantially, outlet valve is located static once more closing one second crank angle in pre-scavenging phase place.Because the maximum pressure differential between firing chamber and air inlet receiver depends on this crank angle, close once more in pre-scavenging phase place at this place, crank angle outlet valve, in pre-scavenging phase place, discharging the amount of fresh air of introducing in the firing chamber after the scavenging groove and controlling and/or regulate according to one or more running parameters of reciprocating internal combustion engine.The volume that seals in the firing chamber by piston in cylinder to the further motion of lower dead point position direction and increase.Because exhaust valve closure, so the pressure in the firing chamber is fallen under the force value in the air inlet receiver, when piston release scavenging groove, scavenging arrives the firing chamber of cylinder through described air inlet receiver with air.At a place, the 3rd crank angle that limits the end of this pre-scavenging phase place, this piston finally discharges the scavenging groove at least in part, thereby scavenging can flow into the firing chamber from the air inlet receiver with air, and outlet valve still keeps closing.Scavenging with air owing to the negative pressure that produces corresponding to the air inlet receiver in pre-scavenging phase place in the firing chamber is inhaled into the firing chamber.This means, be subjected to the support of the negative pressure that in the turgor movement process of piston in pre-scavenging phase place, in the firing chamber, produces in the turbosupercharger of scavenging being introduced the firing chamber of cylinder with air by the air inlet receiver under the predefined pressure in its function aspects.
Outlet valve is opened near lower dead point position the time once more, thereby the waste gas that the part in the waste gas still is retained in after this pre-scavenging phase place in the firing chamber of cylinder in the compression cycle below (following and burning) can be supplied with pressure booster set by outlet valve through flue gas leading in known manner.
When reciprocating internal combustion engine arrived rotational speed limit, for example after the restarting of motor, turbosupercharger produced enough power, and reciprocating internal combustion engine need not pre-scavenging phase place and just can work after a well-known two-stroke process.Reciprocating internal combustion engine can certainly the method according to this invention work in concrete application the when surpassing rotational speed limit.
The moment that outlet valve activated, be i.e. in moment of opening or closing of outlet valve, can be independent of the crank angle and freely select.For large-scale diesel engine, be possible for example with the ECU (Electrical Control Unit) that replaces camshaft.The actuating of outlet valve by a freedom control unit able to programme according to the rotating speed of temperature in the firing chamber of gas pressure in the firing chamber of the rotating speed of reciprocating internal combustion engine and/or crank angle and/or cylinder and/or cylinder and/or pressure booster set and/or the gas pressure in the pressure booster set and/or the temperature in the pressure booster set and/or according to other running parameter control of reciprocating internal combustion engine and/or regulate.
In another embodiment of the method according to this invention, scavenging is carried out with the suction valve that enters in the cylinder head that preferably is contained in large-scale diesel engine by of air to the firing chamber of cylinder.In this method according to this invention variations, the moment that suction valve activated, be i.e. in suction valve moment of closing or opening, can be independent of the crank angle and freely select.Because the maximum pressure differential between firing chamber and air inlet receiver depends on the crank angle equally, open when pre-scavenging phase place finishes at this place, crank angle suction valve, so the amount of fresh air after pre-scavenging phase place in the firing chamber of inflow cylinder can be opened when the scavenging phase place finishes in advance at this place, crank angle suction valve by suitable selection control and/or the adjusting to the crank angle.The actuating of suction valve, the actuating of example exhaust valve is such, by a freedom control unit able to programme according to the rotating speed of temperature in the firing chamber of gas pressure in the firing chamber of the rotating speed of reciprocating internal combustion engine and/or crank angle and/or cylinder and/or cylinder and/or pressure booster set and/or the gas pressure in the pressure booster set and/or the temperature in the pressure booster set and/or according to other running parameter control of reciprocating internal combustion engine and/or regulate.The actuating of suction valve also can and/or be regulated by a freedom control unit control able to programme certainly, but can for example pass through other device, and for example mechanism arrangement is carried out.
According to two-stroke reciprocating combustion engine of the present invention, particularly a kind of large-scale diesel engine, its the method according to this invention work, and it comprises a cylinder and a pressure booster set, cylinder has an outlet valve and at least one scavenging air openings, in cylinder, be furnished with one and can between a lower dead point position and a upper dead center position, move surperficial pistons reciprocating along one, pressure booster set has one by the exhaust-driven turbine from the firing chamber of cylinder, pressurized air is supplied with the firing chamber of cylinder with air openings by a scavenging with air as scavenging.
Description of drawings
Illustrate in greater detail the present invention below in conjunction with accompanying drawing.Accompanying drawing is depicted as:
Fig. 1 has schematically illustrated a pith that has the two-stroke large internal-combustion engine of a pressure booster set;
Fig. 2 has schematically illustrated according to one embodiment of the method for the invention a kind of; With
Fig. 3 has schematically illustrated the cylinder that has a suction valve of a two-stroke large internal-combustion engine.
Embodiment
Fig. 1 has schematically illustrated a pith that has the two-stroke large internal-combustion engine of a pressure booster set 7, and this pressure booster set has the two stroke engine that prolongs scavenging as one and as a global design of representing with reference number 1 hereinafter.
Large-scale diesel engine 1 generally includes several cylinders 2, this cylinder has a cylinder head 21 and an outlet valve 4 that is arranged in the cylinder head, being furnished with one in cylinder 2 can be along surperficial 6 pistons reciprocating 5 of operation between a lower dead point position UT and upper dead center position OT, and the upper dead center position OT of piston 5 is as usual with the crank angle K of 0 ° or 360 °
WExpression, the lower dead point position UT of piston 5 is as usual with one 180 ° crank angle K
WExpression.Cylinder 2 and cylinder head 21 and piston 5 limit a firing chamber 22 by mode.In the lower area of cylinder 2, be provided with several scavengings that are designed to scavenging groove 41 air openings 4.Scavenging groove 41 is covered according to the position of piston 5 and by piston or by piston release.Can be with the fresh air that scavenging is represented with air 12 through the firing chamber 22 of scavenging groove 41 inflow cylinders 2.The waste gas that produces in the firing chamber 8 is through being arranged in outlet valve 3 in the cylinder head 21 through flowing into a pressure booster set 7 with the adjacent flue gas leading 13 of outlet valve 3.Pressure booster set 7 includes a rotor 10 and a turbine 9 that is used to drive rotor 10 that is used for pressurized air 11 as important component by known way, and rotor 10 is connected with a kind of effective means of fixation by an axle 91 with turbine 9.Turbine 9 and rotor 10 are arranged in the housing and constitute a turbosupercharger 14.Turbine 9 is owing to the inflow from the hot waste gas 8 of the firing chamber 22 of cylinder 2 is driven.In order to use the firing chamber 22 of air 12 supercharging cylinders 2 with scavenging, air 11 is inhaled into and is compressed in turbosupercharger 14 through a sucking pipe 15 by rotor 10.Pressurized air moves to the air inlet receiver 19 through a pressure piping 18 by a downstream diffuser 16 and an air-cooler 17 from turbosupercharger, and the air that compression ends enters the firing chamber 2 of cylinder 2 with air openings 4 from this by the scavenging that is formed with scavenging groove 41 with air 12 as scavenging under the pressure that increases.
According to two-stroke reciprocating combustion engine 1 of the present invention be in low speed the time method of work, this speed is lower than the predefined rotational speed limit that is used for a kind of two-stroke large diesel engine 1 that schematically illustrates among a Fig. 2.In order to explain the important step that is used to carry out the method according to this invention, figure 2 illustrates a complete two stroke cycle.In a complete two stroke cycle at the crank angle of eight selections K
WThe place shows the position of cylinder 2, wherein 0 ° crank angle K
WCorresponding to the upper dead center position OT of piston 5,180 ° crank angle K wherein
WLower dead point position UT corresponding to piston 5.Because the method according to this invention is a kind of two-stroke method, so 0 ° crank angle K
WEqual 360 ° crank angle K
W
At a crank angle K
1The place, the burning in the firing chamber 22 of cylinder 2 is finished after the compression cycle of a front substantially, thereby can obtain being in the hot combustion gas under the working pressure in firing chamber 22, thereby makes piston 5 in the cylinder 2 from crank angle K
1The place begins in an expansion cycle to the crank angle K corresponding to 180 °
WLower dead point position UT direction motion.Outlet valve 3 is at crank angle K
1The place closes.One carrying out that fuel sprays and with after-combustion after and among the pre-scavenging phase place V that scavenging enters the firing chamber 22 of cylinder 2 subsequently with air 12 before, begins, promptly piston 5 discharges scavenging groove 41 for the first time after a burn cycle before and at a crank angle K
2The place, outlet valve 3 is opened along with the beginning of pre-scavenging phase place V, i.e. crank angle K
2Be so to select, thereby work as outlet valve at crank angle K
2The place is when opening, and pressure still remains on the pressure in the flue gas leading 13 well in the firing chamber 22 of cylinder 2.Because the pressure difference between firing chamber 22 and flue gas leading 13, hot waste gas 8 flows into turbosupercharger 14 by flue gas leading 13, and at that driving turbine 9, thereby drive rotor 10, as mentioned above, can obtain as the scavenging of the firing chamber 22 that is used for introducing cylinder 2 pressurized air with air 13, the scavenging groove 41 of this cylinder is discharged by corresponding piston 5 simultaneously.This means, the part in the heat energy of waste gas 8 by known way be utilized, by before discharging scavenging groove 41, promptly before the firing chamber 22 of scavenging, open outlet valve 3 and driven the turbine 9 of turbosupercharger 14 with air 12 inflow cylinders 2.
At one slightly greater than crank angle K
2Crank angle K
3The place, the pressure difference between firing chamber 22 and the flue gas leading 13 is balance basically, outlet valve 3 in pre-scavenging phase place V at crank angle K
3Locate static once more closing.Because the maximum pressure differential between firing chamber 22 and air inlet receiver 19 depends on crank angle K
W, outlet valve 3 is being closed in pre-scavenging phase place V once more at place, this crank angle, is discharging scavenging and introduce amount of fresh air in the firing chamber 22 after with air openings 4 by crank angle K in pre-scavenging phase place V
WPredefined value according to the rotating speed of reciprocating internal combustion engine 1, according to crank angle K
WAnd/or the rotating speed of temperature in the firing chamber 22 of gas pressure in the firing chamber 22 of cylinder 2 and/or cylinder 2 and/or pressure booster set 7 and/or the gas pressure in the pressure booster set 7 and/or the temperature in the pressure booster set 7 and/or according to other running parameter control of reciprocating internal combustion engine 1 and/or regulate, closing in pre-scavenging phase place V at this place, crank angle outlet valve 3.The volume of sealing is increased to the further motion of lower dead point position UT direction in cylinder 2 by piston 5 in the firing chamber 22, thereby the pressure in the firing chamber 22 is closed under the pressure of falling in the air inlet receiver 19 owing to outlet valve 3.At a crank angle K who is marking the end of pre-scavenging phase place V
4The place, piston 5 discharges scavenging groove 41 at least in part, thereby scavenging can flow out air inlet receiver 19 and enter firing chamber 22 with air 12, outlet valve 3 still keeps closing.Scavenging with air 12 owing to the negative pressure that produces at pre-scavenging phase place V in the firing chamber 22 is inhaled into firing chamber 22.This means, be subjected to the support of the negative pressure that in the turgor movement process of piston 5 in pre-scavenging phase place, in firing chamber 22, produces in the turbosupercharger 14 of scavenging being introduced the firing chamber 22 of cylinders 2 with air 12 by air inlet receiver 19 under the predefined pressure in its function aspects.
At a crank angle K near lower dead point position UT
5Place and before or after piston 5 arrives lower dead point position UT, outlet valve 3 is opened, thus waste gas 8 can be supplied with pressure booster set 7 through flue gas leading 13 by outlet valve 3 in the compression cycle below.At place, one 180 ° crank angles, outlet valve 3 is still to be opened, and a compression cycle begins in a kind of known mode, arrives a crank angle K
6The time scavenging groove 41 is closed, in compression cycle, arrive crank angle K at one as required
6Before or after the predefined time, promptly close outlet valve 3 through after the lower dead point position UT at piston.In another kind of flexible program according to the present invention, outlet valve 3 also can particularly be closed before piston has arrived lower dead point position UT after discharging scavenging port 4 once more.By the further motion of piston 5 to upper dead center position OT direction, the air that is enclosed in the firing chamber 22 is compressed, fuel was introduced in the firing chamber 22 by a nozzle (not shown) in a well-known manner a predefined time, next was the burning of fuel/air mixture in firing chamber 22.
In this respect, the actuating of outlet valve 3 can be by a freedom control unit (not shown) able to programme according to the rotating speed of reciprocating internal combustion engine 1, according to crank angle K
WAnd/or the rotating speed of temperature in the firing chamber 22 of gas pressure in the firing chamber 22 of cylinder 2 and/or cylinder 2 and/or pressure booster set 7 and/or the gas pressure in the pressure booster set 7 and/or the temperature in the pressure booster set 7 and/or according to other running parameter control of reciprocating internal combustion engine 1 and/or regulate.
Method of work according to two-stroke reciprocating combustion engine 1 of the present invention can certainly be successfully used to large-scale diesel engine, it has the suction valve 42 of the scavenging of conduct in the operation surface 6 that replaces cylinder 2 with the scavenging groove 41 of air openings 4, as shown in Figure 3.Carry out the method according to this invention with a reciprocating internal combustion engine 1 that has a suction valve 42 in a similar manner.Yet, although have for the longitudinally scavenged large-scale diesel engine 1 for one, scavenging with the release of air openings 4, be that the release of scavenging groove 41 is predetermined by the position of the piston in the cylinder 25, but for a large-scale diesel engine 1 with suction valve 42, suction valve 42 still must be activated by a control gear.The actuating of suction valve 42 preferably by a freedom control unit (not shown) able to programme according to the rotating speed of reciprocating internal combustion engine 1, according to crank angle K
WAnd/or the rotating speed of temperature in the firing chamber 22 of gas pressure in the firing chamber 22 of cylinder 2 and/or cylinder 2 and/or pressure booster set 7 and/or the gas pressure in the pressure booster set 7 and/or the temperature in the pressure booster set 7 and/or according to other running parameter control of reciprocating internal combustion engine 1 and/or regulate.
As mentioned above, preferably use the method according to this invention of previous explanation under the rotating speed in low loading range that is lower than a predefined rotational speed limit.When reciprocating internal combustion engine 1 surpassed this rotational speed limit, when turbosupercharger 14 has reached a predefined power, reciprocating internal combustion engine 1 just according to one from the known two-stroke method work of prior art.
By using the method according to this invention, avoided and the relevant shortcoming of use that is used for when hanging down loaded work piece, supporting the additional hydraulic booster of exhaust-gas turbocharger.Like this, not only avoided additional hydraulic booster, but also avoided being used to control the effort of purchasing and installing of its required device.It is uncomplicated that the design of air inlet receiver also becomes, and this is also can be removed because the form particularly in this air inlet receiver is the backflow block piece of sheet shaped piece.Can save the service relevant equally and repair effort with the surcharge of working resource, machine accessory and manpower.Particularly, by using the method according to this invention can save a large amount of spaces and weight.In addition, say from energy point of view.The work that does not have the reciprocal internal-combustion engine of assisted turbocharger also is more favourable, because no longer need to obtain being used for the electric energy of their work, and can save final weight.Considerable is that the use of the method according to this invention causes the fuel consumption of reciprocating internal combustion engine to reduce.
Claims (9)
1. the method for work of a two-stroke reciprocating combustion engine (1), particularly a kind of large-scale diesel engine, it comprises:
-one cylinder (2) with an outlet valve (3) and scavenging usefulness air openings (4), in cylinder (2), be furnished with one can be between a lower dead point position (UT) and a upper dead center position (OT) along operation surface (a 6) pistons reciprocating (5) and
-one pressure booster set (7), it has the turbine (9) and the rotor (10) that is used for pressurized air (11) that are driven by the waste gas (8) from the firing chamber (22) of cylinder (2), pressurized air is supplied with the firing chamber (22) of cylinder (2) with air openings (4) by a scavenging with air (12) as scavenging
It is characterized in that, carry out that fuel sprays and with after-combustion after and in firing chamber (22) that scavenging enters cylinder (2) subsequently with air (12) before, outlet valve (3) is opened earlier when being lower than at least one predefined rotational speed limit and then is closed in a pre-scavenging phase place (V).
2. the method for claim 1, wherein outlet valve (3) is only just opened earlier and then is closed when being lower than this predefined rotational speed limit of reciprocating internal combustion engine (1) in pre-scavenging phase place (V).
3. method as claimed in claim 1 or 2, wherein, the actuating of outlet valve (3) is by rotating speed and/or the crank angle (K of a freedom control unit able to programme according to reciprocating internal combustion engine
W) and/or the firing chamber (22) of cylinder (2) in gas pressure and/or the rotating speed of temperature in the firing chamber (22) of cylinder (2) and/or pressure booster set (7) and/or the gas pressure in the pressure booster set (7) and/or the temperature in the pressure booster set (7) and/or according to other running parameter control of reciprocating internal combustion engine (1) and/or regulate.
4. the method according to any one of the preceding claims, wherein, the firing chamber (22) of cylinder (2) is supplied with in scavenging with air openings (4) by the scavenging of the scavenging groove (41) in the operation surface (6) that forms cylinder (2) with air (12).
5. as each described method among the above-mentioned claim 1-3, wherein, scavenging is controlled and/or is regulated with the suction valve of being located with air openings (4) by scavenging (42) that enters of air (12) in the firing chamber (22) of cylinder (2).
6. method as claimed in claim 5, wherein, the actuating of suction valve (42) is by rotating speed and/or the crank angle (K of a freedom control unit able to programme according to reciprocating internal combustion engine
W) and/or the firing chamber (22) of cylinder (2) in gas pressure and/or the rotating speed of temperature in the firing chamber (22) of cylinder (2) and/or pressure booster set (7) and/or the gas pressure in the pressure booster set (7) and/or the temperature in the pressure booster set (7) and/or according to other running parameter control of reciprocating internal combustion engine (1) and/or regulate.
7. as claim 5 or 6 described methods, wherein, the actuating of suction valve (42) is by a machine control unit, particularly by Control Shaft control and/or adjusting.
8. the method according to any one of the preceding claims, wherein, in a compression cycle, outlet valve (3) is opened near lower dead point position (UT) time, arrives crank angle K at one then
6Before or after the predefined time close once more.
9. a two-stroke reciprocating combustion engine (1), particularly a kind of large-scale diesel engine, it comprises a cylinder (2) and a pressure booster set (7), cylinder (2) has an outlet valve (3) and a scavenging air openings (4), being furnished with one in cylinder (2) can be along operation surface (a 6) pistons reciprocating (5) between a lower dead point position (UT) and a upper dead center position (OT), pressure booster set (7) has a turbine that is used for pressurized air (11) (9) that is driven by the waste gas (8) from cylinder (2), pressurized air is supplied with the firing chamber (22) of cylinder (2) with air openings (4) by a scavenging with air (12) as scavenging, it is characterized in that each described method work among reciprocating internal combustion engine (1) basis as the above-mentioned claim 1-8.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP02405578 | 2002-07-09 | ||
| EP02405578.2 | 2002-07-09 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1472425A true CN1472425A (en) | 2004-02-04 |
| CN100538043C CN100538043C (en) | 2009-09-09 |
Family
ID=30129266
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031471935A Expired - Fee Related CN100538043C (en) | 2002-07-09 | 2003-07-08 | The method of work of two-stroke reciprocating combustion engine |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP1380737B1 (en) |
| JP (2) | JP2004044593A (en) |
| KR (1) | KR101061862B1 (en) |
| CN (1) | CN100538043C (en) |
| DE (1) | DE50300453D1 (en) |
| DK (1) | DK1380737T3 (en) |
| PL (1) | PL361130A1 (en) |
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| CN101501310B (en) * | 2006-08-04 | 2011-06-22 | 丰田自动车株式会社 | Direct injection type spark ignition internal combustion engine and fuel injection method thereof |
| CN101353979B (en) * | 2007-07-27 | 2012-10-03 | 瓦特西拉瑞士股份有限公司 | Two-stroke diesel combustion engine |
| CN102777248A (en) * | 2012-08-01 | 2012-11-14 | 陈卫文 | Two-stroke diesel engine |
| CN103026034A (en) * | 2010-08-05 | 2013-04-03 | 株式会社Ihi | Two-stroke engine |
| CN101666259B (en) * | 2008-09-03 | 2013-07-24 | 瓦特西拉瑞士股份有限公司 | Method for operating a longitudinally scavenged two-stroke large diesel engine |
| CN103249939A (en) * | 2010-12-09 | 2013-08-14 | 日立造船株式会社 | Two-stroke engine and four-stroke engine |
| CN103782006A (en) * | 2011-09-14 | 2014-05-07 | 三菱重工业株式会社 | Contamination-preventing structure for scavenging-air water droplet separator, and vessel provided with contamination-preventing structure for scavenging-air water droplet separator |
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| JP4234695B2 (en) * | 2005-06-03 | 2009-03-04 | エムエーエヌ・ディーゼル・フィリアル・アフ・エムエーエヌ・ディーゼル・エスイー・ティスクランド | Large multi-cylinder two-cycle diesel engine |
| ATE529619T1 (en) * | 2006-10-30 | 2011-11-15 | Waertsilae Nsd Schweiz Ag | INTERCOOLER FOR A RECIPIENT COMBUSTION ENGINE |
| KR20080074719A (en) | 2007-02-08 | 2008-08-13 | 베르트질레 슈바이츠 악티엔게젤샤프트 | A method for the charging of a cylinder of a longitudinally scavenged two-stroke large diesel engine with charging air, and also a longitudinally scavenged two-stroke large diesel engine |
| DK1956210T3 (en) * | 2007-02-12 | 2012-05-21 | Waertsilae Nsd Schweiz Ag | Process for operating a long-flush large two-stroke diesel engine and long-flush large two-stroke diesel engine |
| EP2098708A1 (en) * | 2008-03-06 | 2009-09-09 | Wärtsilä Schweiz AG | A method for the operation of a longitudinally scavenged two-stroke large diesel engine and a longitudinally scavenged two stroke large diesel engine |
| DK2112349T3 (en) * | 2008-04-21 | 2013-06-24 | Waertsilae Nsd Schweiz Ag | Rinse Performance Monitoring System and Method for Monitoring a Process Parameter for the Rinse Process for a Long Rinsed Large 2-Stroke Diesel Engine |
| DE102010004516B4 (en) * | 2010-01-13 | 2012-11-08 | Bernd Hopke | Method for operating an internal combustion engine |
| FR2991719B1 (en) * | 2012-06-12 | 2016-02-19 | IFP Energies Nouvelles | METHOD FOR SCANNING REDISOUS BURN GASES BY DOUBLE LIFTING OF VALVES FOR A TWO-STROKE ENGINE, IN PARTICULAR OF A DIESEL TYPE |
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| US2820339A (en) * | 1952-03-31 | 1958-01-21 | Nordberg Manufacturing Co | Turbo-charged internal combustion engines and methods of starting and operating them |
| DE1121406B (en) * | 1960-03-15 | 1962-01-04 | Sulzer Ag | Two-stroke internal combustion engine with controlled exhaust valve and exhaust gas turbocharger |
| FR2589518B1 (en) * | 1985-11-06 | 1987-12-24 | Melchior Jean | IMPROVEMENTS ON TWO-STROKE INTERNAL COMBUSTION ENGINES AND METHOD OF IMPLEMENTING |
| EP0579590B1 (en) * | 1992-07-17 | 1996-02-28 | AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH.Prof.Dr.Dr.h.c. Hans List | Two stroke internal combustion engine |
| JP2003138943A (en) * | 2001-10-30 | 2003-05-14 | Daihatsu Motor Co Ltd | Two-cycle internal combustion engine |
| JP7084847B2 (en) | 2018-11-02 | 2022-06-15 | 株式会社トクヤマ | Silica-titania composite oxide particles |
-
2003
- 2003-06-11 EP EP03405416A patent/EP1380737B1/en not_active Expired - Lifetime
- 2003-06-11 DE DE50300453T patent/DE50300453D1/en not_active Expired - Lifetime
- 2003-06-11 DK DK03405416T patent/DK1380737T3/en active
- 2003-06-17 KR KR1020030039158A patent/KR101061862B1/en not_active IP Right Cessation
- 2003-07-07 PL PL03361130A patent/PL361130A1/en not_active Application Discontinuation
- 2003-07-08 CN CNB031471935A patent/CN100538043C/en not_active Expired - Fee Related
- 2003-07-08 JP JP2003193373A patent/JP2004044593A/en active Pending
-
2010
- 2010-03-01 JP JP2010044384A patent/JP2010151140A/en active Pending
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| CN101666259B (en) * | 2008-09-03 | 2013-07-24 | 瓦特西拉瑞士股份有限公司 | Method for operating a longitudinally scavenged two-stroke large diesel engine |
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| CN103249939B (en) * | 2010-12-09 | 2015-09-09 | 日立造船株式会社 | Two stroke engine and four stroke engine |
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| US9404412B2 (en) | 2010-12-09 | 2016-08-02 | Hitachi Zosen Corporation | Two-stroke engine and four-stroke engine |
| CN103782006A (en) * | 2011-09-14 | 2014-05-07 | 三菱重工业株式会社 | Contamination-preventing structure for scavenging-air water droplet separator, and vessel provided with contamination-preventing structure for scavenging-air water droplet separator |
| CN103782006B (en) * | 2011-09-14 | 2017-07-28 | 三菱重工业株式会社 | Clear away the drop separator contamination preventing structure of air and possess the ship of the structure |
| CN102777248A (en) * | 2012-08-01 | 2012-11-14 | 陈卫文 | Two-stroke diesel engine |
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Also Published As
| Publication number | Publication date |
|---|---|
| JP2010151140A (en) | 2010-07-08 |
| JP2004044593A (en) | 2004-02-12 |
| DE50300453D1 (en) | 2005-05-25 |
| EP1380737B1 (en) | 2005-04-20 |
| KR20040005588A (en) | 2004-01-16 |
| PL361130A1 (en) | 2004-01-12 |
| CN100538043C (en) | 2009-09-09 |
| DK1380737T3 (en) | 2005-07-25 |
| EP1380737A1 (en) | 2004-01-14 |
| KR101061862B1 (en) | 2011-09-02 |
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